CN101344099B - Electric driven blower and electric suction cleaner having the same - Google Patents

Abstract

The invention provides an electric blower and an electric vacuum cleaner loaded with it. Due to the level difference in the flow path at the vane inlet, the airflow is temporarily separated, and a dead space is formed before the air flow is attached to the flow path wall surface in the impeller again, and there is a problem that the blower increases in size. In the relative positional relationship in the meridian plane between the front end A of the mouth ring seal provided on the fan cover of the blower for vacuum cleaners and the front end B where the front edge of the blade of the impeller intersects with the shroud wall, point A and When the radial distance of point B is ΔR and the axial distance is Δb, 0°≤(tan ⁻¹ ΔR/Δb)≤29° and ΔR≥0.5 mm are satisfied.

Description

Electric blowing machine and load its electric vacuum cleaner

Technical field

The present invention relates to electric blowing machine and load its electric vacuum cleaner, particularly the structure of the entrance part of air feeder vane wheel.

Background technique

As requirement the suction intensity of force is arranged to electric vacuum cleaner.For under the condition of certain consumption electric power, obtaining high inhalation power, need reduce the airmechanics loss of vacuum cleaner.Wherein, ad hoc requirement reduce the loss as root that produces inhalation power and the gas fan that proportion is bigger in the integral body loss.

The gas fan that uses in vacuum cleaner is to compare the low specific-speed type gas fan of more paying attention to pressure output with air quantity, it is characterized in that the high-speed driving of changeing with per minute about 45000 for miniaturization.Because the Peak Flow Rate of gas fan inside reaches 160m/s, thus do one's utmost to reduce the flow velocity of stream narrowed portion and reduce and square proportional leaf of flow velocity between frictional loss be very important.In addition, in the exploitation of before this gas fan, carried out reducing the effort of the caused leakage loss in gap etc. of the lip-deep disc friction of impeller outer, rotation section and stationary part.

For example, for reducing frictional loss between leaf, and implemented to reduce the blade inlet diameter and the measure that reduces the inlet circumferential speed, relative velocity is descended interimly.In addition, owing to five powers of disc friction and impeller outer diameter, the proportional increase of cube of revolution, so taked by while making the impeller outer diameter downsizing advance high speed rotatingization, and in the measure that still keeps reducing under the situation of certain load disc friction.In addition, as for leakage loss, its major part causes because of flowing in the gap of the rotation section of impeller eye portion and stationary part, thereby example has taked to import the seal construction that used the solid lubrication sealing material etc. like that so that the minimized measure of leakage rate shown in patent documentation 1.

Patent documentation 1: No. the 3119633rd, Japan's special permission

But when dwindling the blade inlet diameter in order to reduce frictional loss between leaf as described above, blade inlet edge and sealed department are apart from becoming near.Though in wheel rotor, flow into from stationary part at the sealed department air-flow, because the difference of height of stream is arranged,, and form the dead angle before adhering to once more on the stream wall in impeller here so air-flow separates for the time being.Therefore, during excessively near sealed department, the blade inlet edge part will be touched in the dead angle at blade inlet edge, although with low relative velocity, the phenomenon that performance can not improve takes place also.Owing to touching the blade inlet edge portion at dead angle, blade can not be worked effectively, so the gas fan loss increases.Get final product though reduce difference of height, when above-mentioned seal construction is set, need certain clearance, thereby be difficult to dwindle difference of height on the border of rotation section and stationary part in order to dwindle the stagnant water territory.In addition, in vacuum cleaner,, not very wise move usually so get rid of above-mentioned seal construction itself because the leakage loss under the not sealing situation is also bigger than frictional loss between leaf.

In addition, vacuum cleaner with gas fan with the component-assembled of punch process light sheet and make.That is, with blade sheet material and sandwich two boss plates of these parts and the sheet material of guard shield plate and so on by riveted joint mutually and assemble with low cost.Because vacuum cleaner gas fan reciprocating operation in the zone in the such high speed rotating territory of 45000 commentaries on classics from the halted state to the per minute, so the repeated load that will be produced at the residual caulking part effect centrifugal force that residual stress arranged, thereby and the situation that exists the stress phase with riveted joint to make this part fracture that impeller is damaged.So when touching blade inlet edge portion at above-mentioned dead angle, existence will also act on time-dependent Air Force at the impeller front edge, and the problem that is easier to damage.

Summary of the invention

The objective of the invention is to address the above problem, and provide and realize reducing the electric blowing machine of impeller loss and having loaded its electric vacuum cleaner.

For achieving the above object, the invention is characterized in, in the meridian plane of the downstream end A of the stream face of the seal construction portion that fan guard side (static side) is possessed and the upper end portion B that is connected with the guard shield plate at impeller side (rotation side) blade inlet edge in the relative position relation, when the difference that is made as Δ R, axial height at the semidiameter with A, B at 2 is made as Δ b, be configured to

0 °≤(tan ^-1Δ R/ Δ b)≤29 ° and Δ R 〉=0.5[mm].

According to the present invention, owing to can be formed on the impeller that does not interfere with blade inlet edge portion near the regional formed dead angle the inlet that the air-flow that separates because of difference of height adheres again to impeller, so can reduce the loss of impeller and improve the inhalation power of vacuum cleaner.

Description of drawings

Fig. 1 relates to the schematic, cross-sectional diagram of the main body of dust collector of one embodiment of the invention.

Fig. 2 relates to the sectional view of the vacuum cleaner of one embodiment of the invention with electric blowing machine.

Fig. 3 relates near the pie graph of impeller port ring portion of one embodiment of the invention.

Fig. 4 is that expression relates to the numerical definiteness scope of one embodiment of the invention and the figure of effect.

Fig. 5 is the figure that expression relates to the special circumstances of one embodiment of the invention.

Fig. 6 relates near the pie graph of impeller port ring portion of another embodiment of the present invention.

Fig. 7 relates to the overall appearance figure of the electric vacuum cleaner of one embodiment of the invention.

Among the figure:

100-electric vacuum cleaner main body; The 106-electric blowing machine; 108-gas fan inlet; The outlet of 109-gas fan; The 201-gas fan; The 202-motor; The 203-housing; The 204-end bracket; 205,608-rotating shaft; 210,303,603-impeller; The 211-diffuser; 213-returns guide portion; 214,309,609 fan guards; 215,300,500,600-choma portion; 216-sealed department, 217-electric blowing machine inlet; 301,601-sealing material fixed component; 302,602-sealing material; 304,504,604-guard shield wall; 305,605-wheel hub wall; 306,606-blade; 307,501,607-blade inlet edge; 310,610-difference of height radially; The 311-dead angle; 312,505,612-blade inlet edge upper end portion; 313,613-air-flow; 314,614-stationary part front end; 315,615-impeller port ring portion; 316, the axial difference of height of 616-; 506-stationary part end points

Embodiment

Use accompanying drawing that embodiments of the invention are described below.

Embodiment 1

Fig. 7 relates to the overall appearance figure of the electric vacuum cleaner of one embodiment of the invention.

Mark 100 is the electric vacuum cleaner main bodys of taking in dust precipitation chamber and electric blowing machine, and mark 101 is the hose couplings that are connected and are communicated with dust precipitation chamber with the front portion of electric vacuum cleaner 100, and mark 703 is the flexible pipes that are pivotally connected on the hose coupling 101.One end of flexible pipe 703 is connected on the electric vacuum cleaner main body 100 through hose coupling 101, and is communicated with dust precipitation chamber.Mark 704 is that an end is pivotally connected to the other end of flexible pipe 703 and has the operation unit on hand of the switching member 705 that the running of carrying out vacuum cleaner switches, mark 706 is that an end is connected to the telescopic prolongation pipe of the other end of operation unit 704 on hand, and mark 707 is the suction inlet bodies that are connected to the dust of the other end that prolongs pipe 706 and the dedusting face of suction.

The suction that electric blowing machine produced of vacuum cleaner by in electric vacuum cleaner main body 100, taking in, and the dust transport through prolong the swept surface that pipe 706, flexible pipe 703 will suck below suction inlet body 707 is in dust precipitation chamber.

In the sectional elevation of the main body of dust collector that in Fig. 1, schematically shows, the air stream in the electric vacuum cleaner main body 100 is described.Enter dust precipitation chamber 102 from hose coupling 101 leaked-in airs.In Fig. 1, though expression paper bag 103 is used as the control of dust member, the material of bag without limits.In addition, under the situation of cyclone separator mode, replace paper bag 103 and take in cyclone chamber.Removed the air of most of dust and then, also removed thin dust here with paper bag 103 by filter part 104.Then, air stream flows into motor room 105.Electric blowing machine 106 is erected at motor room 105 through vibration-proof rubber 107, enters the mouth 108 leaked-in airs after boosting from gas fan, discharges from gas fan outlet 109.

Secondly, use Fig. 2 to come electric blowing machine 106 is described.Electric blowing machine 106 is made of gas fan 201 and motor 202.

With regard to motor 202, rotating shaft 205 is supported in the motor casing that is made of housing 203 and end bracket 204, and rotor 206 is installed in the rotating shaft 205.Periphery configuration stator 207 at rotor 206.The electric power of supplying with to rotor 206 transmits by brush 208 and the commutator 209 that is in contact with it.

Gas fan 201 constitutes in fan guard 214 and takes in: the impellers 210 that directly link with above-mentioned rotating shaft 205, the diffuser 211 of outer side setting Monday of impeller 210, with respect to above-mentioned diffuser 211 clip dividing plate 212 and configuration relatively return guide portion 213.Impeller 210 contacts with the sealed department 216 that possesses in fan guard 214 sides substantially in choma portion 215, has the structure of anti-leak.

Air by electric blowing machine inlet 217 near through port ring portion 215 for the time being after, by impeller 210 superchargings and speedup.Then, though air communication is crossed diffuser 211 and roughly turned to 180 °, and flow into its partial pressure rising to returning guide portion 213 in this process thereby air-flow slows down.Passed through to return in the air-flow inflow motor field frame 203 of guide portion 213, and in back discharges such as cooled rotor 206, stator 207, brush 208, commutators 209.

Present embodiment is in the scope of φ 60mm～φ 120mm as the vacuum cleaner of the object impeller outer diameter with electric blowing machine, and maximum number of revolutions is in the scope that per minute 35000～50000 changes.

Secondly, use Fig. 3 to come first embodiment of the invention is described.Fig. 3 is near the figure that amplifies the impeller port ring portion with Fig. 2.Sealing material 302 is fixed through being installed in the sealing material fixed component 301 on the fan guard 309.315 pairs of sealing materials of impeller port ring portion 302 embed, and constitute sealing mechanism.Though it is important that sealing mechanism is in this position, be not limited to this mode.Secondly, blade inlet edge 307 and the point that guard shield wall 304 intersects are called blade inlet edge upper end portion 312.Though suck now and flow into air-flow 313, after stationary part front end 314 separates for the time being, just once more on the guard shield wall 304 attached to the impeller that is positioned at its downstream position along the surface of static fan guard 309.This separated region is schematically shown as dead angle 311.

On the other hand, blade 306 and guard shield wall 304 and wheel hub wall 305 are by riveting parts 317 and fastened to each other.Though prepare a plurality of riveting parts along blade 306 usually, the riveting parts that only is conceived to the most close internal side diameter of guard shield wall side here illustrates.Its reason is, this position is to be vulnerable to the position of interfering with the aerodynamic force at above-mentioned dead angle most, and is the also the most concentrated position of tectonic stress.Promptly, for reducing frictional loss between leaf, blade inlet edge 307 is dwindled under the situation of blade inlet diameter near rotating shaft 308, the distortion of the blade due to the centrifugal force in order to prevent to rotate, and in order to dwindle the scope that becomes cantilever support, and must big part implement riveted joint in the curvature of the internal side diameter of guard shield wall 304, but the riveted joint on this type of curved surface is residual very big residual stress arranged.

The mode that present embodiment is not interfered with blade inlet edge with above-mentioned dead angle concerns with the interior position of the meridian plane of numerical definiteness stationary part front end 314 (being made as an A) and blade inlet edge upper end portion 312 (being made as a B) as following.That is, be made as Δ R at 2, when axial width is made as Δ b, both relation be limited to in the scope shown in the oblique line of Fig. 4 at radially difference of height 310 with these A, B.

In Fig. 4, the straight line of angle limit 400 is by following formula θ _ gap=tan ^-1Angle θ _ the gap of (Δ R/ Δ b) definition is the line of 29 ° of certain values, represents the CLV ceiling limit value of the numerical definiteness of the present embodiment relevant with θ _ gap.By initial point, and the inclination angle is than in the big straight line of angle limit 400, and θ _ gap becomes littler value, compares with the area size of top end points from the stationary part end points to blade inlet edge, and the size at expression dead angle diminishes relatively.

On the one hand, making the limit 401 is that the required clearance delta R=0.5[mm of minimum when preventing to leak the sealed member of usefulness and absorbing impeller port ring portion circle to depart from is inserted in expression] line, from this straight line executable zone is arranged on the right side.More than two straight lines 400 and 401 area surrounded are numerical definiteness zones that the present invention advocates.

Though in design in the past, also carried out being conceived to the design at two places on impeller port ring portion 315 and blade inlet edge upper end portion 312 these rotors, but present embodiment is characterised in that the rotation section that is conceived to blade inlet edge upper end portion 312 and stationary part end points 314 and this two place of stationary part and considers the dead angle, and carried out numerical definiteness as described above.

In Fig. 4, for the gas fan 402 of prior art with implemented a plurality of gas fans 403, the measured value of the raising amount of the gas fan efficient before and after the relation of expression Δ R and Δ b and the control as the control of the Δ R of present embodiment and Δ b.Confirm

Regional efficient improvement.Make θ _ gap then better more though will consider usually, have limit owing to possess on the required size of seal construction, so with the lower limit set of straight line 401 as numerical definiteness than 29 ° more little.

By doing the cost structure, can avoid dead angle and blade inlet edge to interfere, so can improve gas fan efficient.In addition, owing to the non-permanent aerodynamic force that can reduce simultaneously, so can suppress the fracture of caulking part towards blade inlet edge.

Though in Fig. 4, represented the blade inlet edge shape of standard, but near the guard shield wall 504 at blade inlet edge 501 as shown in Figure 5, otch 502 is set or makes blade inlet edge under this another extreme crooked situation, draw auxiliary line 503 as shown in FIG. like that, the point that itself and guard shield wall 504 intersected or describe concentric circle 507 and the point on the nearest blade inlet edge is defined as blade inlet edge upper extreme point 505 from stationary part end points 506.And, adopt a diminish side definition of θ _ gap among both.

In addition, though be prerequisite with gas fan in the present embodiment with the seal construction by other parts, even as dwindled the simple seal structure in the gap of fan guard and impeller, also applicable numerical definiteness scope shown in Figure 4.

Have again, in the embodiment shown in fig. 3,, be not limited to this type of formation though roughly the stationary part end points is set towards axial part at air-flow along fan guard.For example, make that the fan guard side further enters impeller side and the structure of the part of the original impeller guard shield wall of double as, and the stationary part end points is set in than the structure of Fig. 3 more also can by downstream side etc.

Embodiment 2

Use Fig. 6 that second embodiment relevant with the present invention is described below.Though in embodiment 1, because of seal construction produces difference of height, as shown in Figure 6, present embodiment is to possess sealing material 402 and the example of form that the difference of height that arrives seen in the embodiment 1 is eliminated as possible.This formation can be by being that blank is shaped or cutting guard shield wall is realized with thicker sheet material for example.

In this case, though difference of height is almost eliminated,, before air-flow 414 mixing that will flow into, rectification, need identical with embodiment 1 situation apart from this situation from stationary part owing to there be the poor of the such motion state of rotation section and stationary part.In this case, get radial distance delta R and axial distance Δ b as shown in Figure 6 like that, and only use angular range shown in Figure 4.As for effect, identical with embodiment 1.

Claims (6)

1. An electric blower comprising an electric motor, an impeller directly connected to the rotating shaft of the electric motor, a diffuser with blades provided on the outer peripheral side of the impeller, and a fan cover covering the blower part constituted by the impeller and the diffuser . A sealing portion attached to the fan case side at the inlet portion of the impeller, wherein: In the relative positional relationship in the meridian plane between the most downstream end portion A of the flow path wall portion of the fan case and the upper end portion B of the blade leading edge where the blade leading edge of the impeller intersects with the shroud wall, the above-mentioned A and B When the radial distance is set to ΔR and the distance in the direction of the rotating shaft is set to Δb, it satisfies 0°≤tan ^-1 (ΔR/Δb)≤29° and ΔR≥0.5mm. 2. An electric blower comprising an electric motor, an impeller directly connected to the rotating shaft of the electric motor, a diffuser with blades provided on the outer peripheral side of the impeller, and a fan cover covering the blower part constituted by the impeller and the diffuser . A sealing portion attached to the fan case side at the inlet portion of the impeller, wherein: In the relative positional relationship in the meridian plane between the end point A of the inlet ring of the impeller and the upper end B of the blade leading edge where the blade leading edge of the impeller intersects with the shroud wall, the radial distance between the above-mentioned A and B is set as ΔR , When the distance in the direction of the rotating shaft is set to Δb, it satisfies 0°≤tan ^-1 (ΔR/Δb)≤29°. 3. The electric blower according to claim 1 or 2, characterized in that, The motor has an operating range of 35,000 to 50,000 revolutions per minute, and the outer diameter of the impeller is φ60 to 120 mm. 4. An electric vacuum cleaner comprising: an electric vacuum cleaner main body having a dust collection chamber and an electric blower, a hose connected to the electric vacuum cleaner main body, a hand operation part connected to the hose, and an extension pipe connected to the hand operation part , the suction body connected with the extension tube, The electric blower includes a motor, an impeller directly connected to a shaft of the motor, a diffuser with blades provided on the outer peripheral side of the impeller, a fan cover that covers the blower portion constituted by the impeller and the diffuser, and the impeller. The inlet part of the above-mentioned fan cover side is installed in the sealing part, and it is characterized in that, In the relative positional relationship in the meridian plane between the most downstream end portion A of the flow path wall portion of the fan case and the upper end portion B of the blade leading edge where the blade leading edge of the impeller intersects with the shroud wall, the above-mentioned A and B When the radial distance is set to ΔR and the distance in the direction of the rotating shaft is set to Δb, it satisfies 0°≤(tan ⁻¹ ΔR/Δb)≤29° and ΔR≥0.5mm. 5. An electric vacuum cleaner comprising: an electric vacuum cleaner main body having a dust collection chamber and an electric blower, a hose connected to the electric vacuum cleaner main body, a hand operation part connected to the hose, and an extension pipe connected to the hand operation part , the suction body connected with the extension tube, The electric blower includes a motor, an impeller directly connected to a shaft of the motor, a diffuser with blades provided on the outer peripheral side of the impeller, a fan cover that covers the blower portion constituted by the impeller and the diffuser, and the impeller. The inlet part of the above-mentioned fan cover side is installed in the sealing part, and it is characterized in that, In the relative positional relationship in the meridian plane between the end point A of the inlet ring of the impeller and the upper end B of the blade leading edge where the blade leading edge of the impeller intersects with the shroud wall, the radial distance between the above-mentioned A and B is set as ΔR , When the distance in the direction of the rotating shaft is set to Δb, it satisfies 0°≤tan ^-1 (ΔR/Δb)≤29°. 6. The electric vacuum cleaner according to claim 4 or 5, characterized in that, The motor has an operating range of 35,000 to 50,000 revolutions per minute, and the outer diameter of the impeller is φ60 to 120 mm.

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